Pneumatic control system for a laundry machine



p 1964 R. AIBRENNER ETAL 3,151,066

PNEUMATIC CONTROL SYSTEM FOR A LAUNDRY MACHINE Filed Nov. 29, 1960 5Sheets-Sheet 1 m n r H w W w H w d 14 u I r. $3 /2 Se t. 29, 1964 R. A.BRENNER ETAL 3,151,065

PNEUMATIC CONTROL SYSTEM FOR A LAUNDRY MACHINE Filed Nov, 29, 1960 5Sheets-Sheet 2 INVENTORJ Robert a Brenner Clifton d- 6066 L H. 5 M I I(y a auer- EZl Sept. 29, 1964 R. A. BRENNER ETAL 1,

PNEUMATIC CQNTROL SYSTEM FOR A LAUNDRY MACHINE Filed Nov. 29, 1960 5Sheets-Sheet s JNVENTOR Roiert Bnenner (Yd/50114.60fi5 Leo H \Sauer y494% W; and W HU 5 Sheets-Sheet 4 R. A. BRENNER ETAL JNVEMTURJ Ruler!ldffiresr cmr' [ddftan 54- 601.25

PNEUMATIC CONTROL SYSTEM FDR A LAUNDRY MACHINE Filed Nov 29, .1960

Sept. 29, 1964 1 X1354, R :/,,0WM

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,MOTOR United States Patent 3,151,066 INEEJMA it: CONTRQL SYSTEM FOR ALAUNDRY MAiIHlNE Robert A. Erenner, Clifton A. fiohb, and Leo H. Sauer,St. .loseph, Mich, assignors to Whirlpool Corporation,

t. Joseph, Mich, a corporation of Delaware Filed Nov. 29, 1960, Ser. No.72,447 8 tllairns. ('31. 219-144 The present invention relates broadlyto acceleration control systems, and is more particularly concerned witha novel apparatus wherein a horizontal or substantially horizontal axistype drum is limited to a safe optimum rotative speed in response todeflections of the drum due to rotation of unbalanced loads therein.

The principles of the present invention can readily be incorporated inany balancing system and method wherein it is desired to counterbalanceunsymmetrically disposed centrifugal forces generated because ofunbalance in a rotating body, however, because these principles find aparticularly useful application to a laundry machine and method, theinvention is described and illustrated in connection with a specificlaundry machine associated with domestic utilization such as a typicalhome laundry appliance.

In cont mporary domestic laundry appliances, including automatic washingmachines wherein clothes are washed and centrifuged, or in so-calledcombination washer-dryers wherein clothes are washed, rinsed, spun dryand tumbled dry with the application of heat energy, that part of thetotal washing and drying time preceding the tumble dry or line dryportion of the total laundering cycle time is designated as the washportion of the total cycle, and consumes substantially the same amountof actual time for most available machines. Accordingly, to decrease theoverall wash and dry time of a particular load, the most practicalsubstantial time savings can be made by shortening the dry portion ofthe total cycle.

The conventional approach to an attempted improvement of machine dryinginvolves the consideration of increasing the drying heat input to thedryer, which is somewhat undesirable from a standpoint of the rate ofpower consumption and the somewhat increased cost of operation thusincurred, but it is most undesirable from a standpoint of engineeringdesign considerations which are required because of the increased powerinput to the drying means.

A second approach, and which provides the environment for the presentinvention, is made which is desirable not only from a standpoint ofmachine drying, but also from a standpoint of line drying. This is toincrease the rotative cylinder speed used during the extraction part ofthe wash cycle, to thereby remove larger atnounts of water from the loadprior to the beginning of the tumble or line drying. By increasing thespin speed utilized to remove additional water from the load, a powerconsumption rate savings of approximately 8 to times may be accomplishedas compared with the removal of this additional water by the high powerinput drying process.

With properly designed bearing and transmission systems power input isthe primary consideration that has to be made with respect to the limitof spin speed attained in driving a mass about its exact center of mass.An empty laundry receiving cylinder or drum rotated about its bearingaxis parallels an optimum operating condition, but when a load isintroduced into the cylinder, the load is likely to be distributed insuch a manner that the center of mass of the loaded cylinder will notcoincide with the cylinder bearing axis, thereby producing an unbalancedcentrifugal force which is directly proportional to the mass of theunbalanced portion of the total rotating mass, the square of the angularvelocity of such unbalanced mass and the radius of the unbalanced massfrom the axis of rotation of the cylinder.

In addition to affecting the power input necessary to rotate thecylinder or drum, an unbalanced condition causes serious vibrationconditions which are even more pronounced in horizontal machines than invertical axis machines since the unbalanced force directed substantiallyopposite the gravitational forces acting on the machine may besufficiently great to actually lift the machine from its supportingsurface and produce a violent movement colloquially referred to aswalking.

Because of these problems, some contemporary laundry machines of thehorizontal axis type operate at sufficiently limited spin speeds so thatthe unbalanced loads encountered during normal operation at theselimited spin speeds will not produce a suflicient amount of centrifugalforce to bodily lift the machine from its support. It has also beencontemplated in prior art machines to provide control means whereby aspin mechanism will be inactivated in response to excessive motion inthe apparatus, whereupon the drum or cylinder will decelerate to aturnbling speed for redistribution of the contents thereof. In suchprior art machines, the final spin speed is limited to a value such thatthe total amount of liquid centrifugally extracted from the contents ofthe drum or cylinder is much less than is desired. It will be readilyappreciated that all such extra retained liquid is required to beevaporated either by a longer period of evaporation if the goods areline dried or by consumption of an additional supply of heat energy dueto a longer drying period to dry out moisture not removed by a lowerextraction cylinder speed if the goods are machine-dried.

Other forms of balancing mechanisms employed in laundry apparatuscontemplate suspension. of the entire laundry machine along with anadditional mass producing dead weight within the enclosing cabinet on acomplex spring system. Such arrangements depend upon isolation of thesource of vibration, whereupon the suspended system is allowed toviolently vibrate within the enclosing cabinet with the dead Weighttending to minimize the ef fects of the unbalanced centrifugal forces.With such prior art arrangements, it is inevitably necessary that thesize of the enclosing cabinet must be greatly increased or the size ofthe load receiving cylinder greatly reduced to allow for the violentgyratory motions of such system during operation of the machine.

In other forms of prior art machines, eccentric motions of the rotatingbody are sensed and located by relatively complex mechanisms whichcontrol the addition or subtraction of weights from the rotatingcomponents of the machine, thereby to counteract the unsymmetricallydisposed centrifugal forces generated by the unbalanced conditionswithin the cylinder or drum.

In accordance with the principles of the present invention, a drum isjournaled for rotation on a substantially horizontal axis Within acasing rigidly connected to a base frame. A transmission interconnectsthe drum with a drive motor, and the transmission has a low speed ratiofor tumbling fabrics at a lower washing speed and a high speed ratio forrotating the drum at higher extracting speeds for extracting fluids fromthe fabrics in the drum. As a further feature of this invention, thereis provided clutch means for changing the speed ratios of thetransmission, as well as sensing means responsive to movements of thedrum due to rotation of unbalanced loads therein at the high speedratio, for limiting the speed ratio of the transmission to a valuebetween the low and high speed ratios to thereby efiect the rotation ofthe drum at a safe optimum speed above the lower washing speed.

Illustratively, the clutch means may be of the pneumatic type and thesensing means may include bleed off valve means actuated by vibrationsof the drum to reduce the pneumatic pressure on the clutch means wherebythe tion to provide acceleration control apparatus for a rotat- 7 ingreceptacle.

Another object of this invention lies in the provision of anacceleration control system for use with counterbalance control meansand which does not impede the proper functioning thereof.

Still another object of the instant invention is to provide a systemembodying transmission means, clutch means and sensing means, andwherein the structure is so constituted that the sensing means detectsdeflections of a rotating receptacle which are greater than thedeflections which initiate performance of load balancing functions, thesensing means being in control of the clutch means to limit thetransmission speed ratio so that the receptacle rotates at a safeoptimum speed and which is further sufliciently high so that there is nointerference with performance of the load balancing function.

Other objects and'advantages of the invention will become more apparentduring the course of the following description, particularly when takenin connection with the accompanying drawings.

In the drawings, wherein like numerals designate like parts throughoutthe same:

FIGURE 1 is a front elevational view of a laundry machine incorporatingthe principles of the present invention, but with the outer cabinetremoved and with parts broken away and with other parts removed forclarity;

FIGURE 2 is a side clevational view of the machine of FIGURE 1, withportions of the cabinet structure removed for clarity of illustration;

FIGURE 3 is an enlarged fragmentary view constituting a layout ofsensing mechanisms which may be employed to initiate the loadcounterbalancing function and transmission speed ratio limitingfunction;

FIGURE 4 is a cross-sectional view taken substantially along the lineIV-IV of FIGURE 3, but with parts removed in order to show additionaldetails of the construction. of the water balance sensing mechanism ofFIGURE 3;

FIGURE 5 is a more or less diagrammatic view, with portions thereoftaken in section, showing the acceleration control system of this.invention;

FIGURE 6 is a sectional view taken through a twospeed transmissionemployed in the instant invention; and

FIGURE 7, is a diagrammatic representation of certain hydrauliccircuitry incorporated in the illustrated machine.

Reference willfirst be made in the following description to certainstructural details of an exemplary form of combination washer-dryer, andto an illustrative type of water balance system used therewith. However,it Will be readily appreciated that the acceleration control system'ofthis invention is not restricted in its use to the particular structuralorganization shown in FIGURES 1 and 2, nor do its advantages flow onlyfrom use with the particular liquid balance system also appearin in FIG:URES 3 and 4. As well, it will be observed as the description proceedsthat parts not necessary to a description of the instantaccelerationcontrol system have been removed in the interests of clarity.

designated generally by the numeral 14), and comprises an outer cabinetll providing an esthetically appealing enclosure for the machine lit: Inthe manner conventional in the art, access to a treatment zone formedwithin the machine ill is obtained through a suitable opening in theouter cabinet front wall, this front opening being closed by an accessdoor (not shown) during the laundering operation.

Within the outer cabinet 11 is a rigid base structure shown generally at13, and which comprises a channel member 13a to which is fixedly secureda plate 14. The base structure or frame 13 further may be observed fromFIGURES 1 and 2 to include front legs 15 bolted to the channel member13a, and a single rear leg 16 bolted to member 17 which is welded orotherwise secured to rear wall 13a of a generally imperforate outercasing 18.

The casing 18 is connected to and supported on the base frame 13 by afront support plate member 19 which is integrated with a front wall 18bof the casing 18 by welding or similar techniques. The plate member 19is further securely fastened to the plate member 14 of the base frame13, as by bolt means or the like 20.

The rear wall 18a of the casing 18 has a centrally apertured embossedportion 21 cooperable with a support spider 22 connected in firmassembly with the rear wall 18a to rigidly mount a bearing assemblygenerally designated at 23 in which is journaled shaft means (not shown)connected for corotation with a perforate drum or cylinder 24 rotatablewithin the casing 18.

It is to be noted that the connections provided by the parts 14 and 19between the base frame 13 and casing 13 are rigid connections, however,there is sufiicient yieldability in the support structure so that somevery small movement of the casing 1% relative to the base frame 13 mayoccur. The connections afforded by the connection of the plate members14 and 19 to the channel member 13a and the connection of the part 17 tothe casing 18 are suificiently rigid to confine the casing 13 foroscillatory movements about an axis positioned parallel to and locatedbelow the horizontal rotational axis of the drum 24 prescribed by theconnecting shaft means. In the machine exemplified in the drawings, suchallowable arcuate movement is approximately 0.010 inch from its normalcentered position as measured from an approximate 16 inch lever arm.

The machine 16 is equipped with an electric drive motor 25 which ismounted on the casing is and is provided with a power take-01f shaftdrivingly connected with a transmission 26 which is also mounted on thecasing 13. The transmission 26, which will be later described in morespecific detail, has a take-off shaft 26a (FIGURE 2) mounting pulleys2'7 and 2%, the pulley 27 having trained thereabout a pulley belt 29driving a pulley wheel 35 to rotate the drum 24. The pulley 28, on theother hand, is wrapped by a pulley belt 31 connecting with blower means(not shown) to circulate heated drying air through the drum 24. 7

Machine 1' 3 is further equipped with aconventional mixing valvearrangment (not shown) as well as a sump 149 formed in the lower portionof casing 18 for receiving fluids for the washing, rinsing andextraction operations. Sump 149 communicates with pump 141 which in turnis connected to a first two-way valve 142 which leads either to drainfor pump out operations or to a second two-way valve 143 which isprovided with one conduit 14 for recirculating washing fluid throughdrum 24 during the washing operation by way of a recirculation nozzle(not shown) and a second conduit 32 leading to nozzle 68 forrecirculating balancing fluid through nozzle opening 68a during theextraction operation which balancing fluid is supplied to the fluidreceiving pockets 39 by way of the respective collector segments 4551-0communicating with these pockets. A conventional type sequentialcontroller or timer 33 regulates the operation of valves M2 and 143throughout a programmed se quence.

it will be understood that the sequential control means shown generallyat 33 is presettable by the operator and is associated with the usualelectrical circuitry with all of the operating components of themachine, including the electric drive motor 25, the various valve meansemployed, and particularly solenoid valve means to be later described indetail which is in control of the pneumatic clutch means forming a partof the transmission 26. The sequential control means 33 by the variouselectrical connections conventionally employed actuates the machinethrough a program consisting of washing, rinsing, extracting and dryingperiods. In a typical operation, the operator will load a batch ofclothes to be laundered through the access door into the drum 24, andupon initiation of a preselected program, the casing 18 will be chargedwith a supply of Water. Following the washing operation, the laundryliquid will be drained through the sump and discharged to drain, and thematerials within the drum 24 are then subjected to an extractionoperation, followed by rinsing and a subsequent extraction operation,which portions of the washing cycle may be repeated as often as may bedesired in accordance with the preset program. After the finalextraction operation, the machine either continues through a dryingperiod involving operation of the drying system and including theaddition of heat of vaporization to the stream of ventilating aircirculated through the treatment zone, or the batch of materials beinglaundered may be removed from the machine by the operator ror linedrying.

As earlier indicated, the acceleration control system of this inventionmay be employed in connection with various types of water balancesystems, however, one particularly advantageous balance system is shownin the application drawings in order to clearly illustrate the numerousnovel results obtained by the instant acceleration control system. Inthis connection, it is to be observed from FIGURE 1 that the drum 24 hasformed along its back wall 24a a plurality of radially extending andangularly spaced strengthening ribs 34. At the center of the back Wall2441, the drum 24 is connected as at 35 to shaft means as journaled inthe bearing assembly 23. The outer peripheral wall of the drum 24 isformed by a foraminous Wrapper 3'7 and is particularly characterized bya plurality of openings 38 through which liquid may escape from theinterior of the drum 24 into the casing 18. The drum periphery isfurther provided at a plurality of circumferentially spaced locationstherealong with recess means provided to accommodate mounting therein ofa liquid balancing receptacle indicated generally in FIGURE 2 at 39.Each receptacle 39 comprises a generally trough-shaped tray memberhaving radially spaced walls 40 and 41, axially spaced end Walls 42 and43 and a pair of spaced side walls 44. Each receptacle 39 is providedwith an inlet segment 45a, 45b and 45a which may be seen to be ofgenerally U-shaped configuration and each provided with an opening 46through which all of the fluid within the inlet segment is dischargedradially outwardly into a particular receptacle as required forcounterbalancing purposes. In the exemplary disclosure illustrated,there are three receptacles 39, and accordingly, each segment 45ac may,if desired, extend through 120 of are on the front wall of the drum 24.The inlet segments, generally designated by numeral 45, are attached infirm assembly as by welding or the like to the drum front wall inregister with the liquid supply means provided to introduce balancingfluid thereinto.

in order to control the introduction of balancing fluid into thereceptacles 39 by way of the inlet segments 450-0, there is desirablyutilized as a controlling variable a mechanical signal manifested as arelatively small linear movement between the casing 18 and a relativelystationary reference means. As appears in FIGURES 1 and 3, a balance andnozzle housing 47 is provided with an aperture 48 forming an upper wall49 constituting a surface portion movable in unison with the casing 18.Fastening means 50 may be employed to secure the balance and nozzlehousing 47 to the front wall 18b of the casing 18.

in order to provide a relatively stationary reference with respect tothe housing 47, there is utilized a subframe Sll (FIGURE 1) including anoblique leg 52 fastened in firm assembly with the base frame 13 at 53,as well as a vertical leg 54 secured to the base frame at 55. Thereference means may be seen from FIGURE 3 to further include a slidemember 56 fastened to the A-shaped subframe 51 as at 57, the slidemember 56 having an arm 58 to which is connected a slide block 59 havinga hard ened surface confronting the Wall 4% of the balance and nozzlehousing 47, and closely spaced and in parallel relation thereto.

For the purpose of sensing oscillatory movements of the casing 18 whichare produced as a function of any unbalance manifested within therotating drum 24, there is desirably utilized a sensing member in theform of a reliable pin 64 confined between the surfaces 49 and 59.

lthough not shown in specific detail, the surface 49 is particularlycharacterized by a niche or grooved slot which has width slightly largerthan the outer diameter of the rollable pin 60 to provide the necessaryclearance. If desired, the mentioned slot may receive therein a hardenedinsert 4% to present a surface for engagement against the peripheralsurface of the pin 64 As is believed now quite apparent, the curvedsurface of the pin 60 is on a fixed radius with respect to thecenterline axis of the pin and, therefore, the relative linear movementproduced between the surfaces 49 and 5? is. converted by the sensingmember or pin 69 into angular movments about the pivot axis of the pinby the rolling action of said pin between the relatively moving surfaces59 and 49.

In order to assure that the pin as is tightly confined between thesurfaces 49 and 59, a plurality of spring means 51 are confined by boltmeans 62 and a nut extending between a bottoming plate 63 andembossments 64 on the slide member 59.

The angular movements of the pin 60 are amplified through a moment armprovided by an interrupter or flag member 66 connected in firm assemblywith one end of the pin oil. The connection may be accomplished bywelding the pin to the interrupter member, and it may be observed thatthis member extends generally parallel to the front wall 18b of thecasing 13 and is closely spaced to a splash housing 67 mounted on theinside surface of the front wall 18b between the casing 18 and drum orcylinder 24. The splash housing 67 has formed therein a slotted opening67a and mounted in register therewith is a nozzle member 68 connectingwith the conduit 32, and particularly characterized by a narrowelongated nozzle outlet 68a in discharging register with the slot-tedopening 674: in the splash housing 57.

Both the nozzle discharge outlet 6&1 and the slotted opening 67a arelocated directly adjacent to the arcuate path of movement of theinterrupter member 66. Accordingly, the movements of the casing producedas a function of any acentric disposed load in the rotating drum 24 aresensed in a linear motion of the surfaces 49 and 59, whereupon therolling pin 60, which is forcefully and resiliently squeezed between aportion of the front of the casing 18 and the vertical stationaryextension 51 of the base frame 13, will convert such movements intoangular displacement. The rolling pin 6% provides a pivotal axis for theWater deflector member or interrupter flag 66, which is normallypositioned in the path of a fluid stream discharged through the nozzleoutlet 68a during extraction operations. The deflection means providedby the interrupter member 66, which is located within the casing 18 onthe rear side of the casing front wall 13b and spaced from both thecasing front wall and the splash housing 67, will serve to deflect anddirect the stream emanating from the nozzle outlet 68a downwardly in thesplash housing 67 for return to the casing 18. The

opening 67a in the splash housing 67, as well as the nozzle opening 680,are aligned with the three inlet segments 45a-c carried on the front ofthe drum 24.

In operation, the movements of the casing 18, due to the rotation ofunbalanced loads within the drum, cause a pivotal movement of theinterrupter member 66 away from the fluid stream emanating from thenozzle opening 68a so that the fluid may be injected directly into anappropriate inlet segment 45 for passage to the correct fluidreceivingpocket or compartment provided by a corresponding receptacle 39 on thedrum 24 for automatically counteracting the unbalanced load causing thearcuate movement of the casing.

As was earlier stated, the described water balance system isillustrative of a typical arrangement which can be employed inconjunction with the acceleration control system of this invention.During the course of the following description, which is directedparticularly to a new and improved system for controlling drumacceleration in response to deflection of the cylinder or drum structurerelative to stationary base structure, it will be readily apparent thatother types of water balance systems can be effectively utilized.

Briefly stated, in the acceleration control system of this invention apressturized fluid-operated system comprising a double acting air bleedoff or relief valve is mounted on the stationary A-frame structure 51 tosense vibrations caused by rotation of an unbalanced load in the drum24. The valve connects with an outlet port of a solenoid operated airvalve means and is constructed to provide a pressure bleed off linebetween an air compressor and the air cylinder in control of slip clutchmeans in'the transmission 26. Compressed air from a suitable source iscommunicated to an inlet port in the solenoid valve means, and thesolenoid is energized to accelerate drum 24 from tumble to spin speed bypressurizing a chamber within the solenoid valve means leading to thepneumatic clutch. When an off-balance load is accelerated and produces adeflection, the bleed off valve on the stationary A-frame isintermittently opened to reduce the pressure in the solenoid valvechamber, which through the outlet port leading to the clutch aircylinder, slips the clutch to prevent increased drum acceleration untilthe off-balance load is counterbalanced. However, and as will be pointedout in detail hereinafter, the drum rotative speed is not necessarilyreduced, but is maintained at essentially the speed which caused thecasing deflections so that there is no interference with accomplishmentof the proper water balancing function.

The acceleration control system of this invention is more or lessdiagrammatically illustrated in FIGURE 5, and it may be seen therefromthat the drive motor 25 connects with the transmission means as havingan output shaft 26a mounting the pulleys 27 and 2S constituting theoutput of 'FTGURE 5. The structural details of the transmission meanswill be later described, and for the present purposes it may be notedfrom FIGURE that conduit means 7%) is i n" communication with thetransmission means (specifically a clutch actuated air cylinder thereinwhich will also be later described) and an outlet port 71 of solenoidair valve means generally designated by the numeral 72. A compressor730i any suitable construction has corinected'to the outlet port thereofconduit means 74 leading to an inlet port '75 of the solenoid valvemeans 72. The solenoid Valve means is further provided with a secondoutlet port i6 which communicates through conduit means 77 with a doubleacting bleed off or relief valve means designated generally by thenumeral 78.

The solenoid valve means '72 is provided with a body portion 79 havingat one end thereof a plurality of threaded openings tltla, Sill; andbile receiving coupling members l(l, 81b and 810, respectively, whichare internally bored to provide the outlet port '76, inlet port '75 andoutlet port '71;

The body portion 7'9 of the solenoid valve means 72 till is shapedinteriorly to provide a chamber 82 communi eating with the ports 76, and'71 through reduced diameter passages 76a, 75a and 71a. The chamber 82communicates with a chamber $3 through a central aperture 84a. in arigid diaphragm member 84, which is further provided with vent passages84b leading through vent passages 79a in the body portion 79 toatmosphere.

The central aperture 84a in the rigid diaphragm member 84 receives agenerally T-shaped flat surfaced valve member 86 positioned for contactwith a solenoid armature 37 when solenoid 88 is ale-energized. It may benoted from FIGURE 5 that the solenoid armature 87 has a central axialpassage 87a and bottoming at one end thereof is spring means 89 whichalso bottoms against a fixed plug member 9% having a passage 90atherein. The plug member 96 may be secured in any suitable manner to asolenoid housing 91, and if desired, seal means 92 may be locatedbetween the solenoid armature 37 and plug member 90.

The energization of the solenoid 88 of the solenoid valve means '72controls the shifting of the two speed transmission 26 from tumble tospin speeds. When the solenoid is de-energized, the spring loadedsolenoid armature 87 assumes its uppermost position which forces thevalve member 36 against surface 82a, which in turn permits cavity orchamber 82 to be vented to atmosphere through the vents or passages 84a,84b and 79a in the rigid diaphragm 8d and body portion 79, respectively.This action prevents the air pressure from the compressor 73 fromreaching the pneumatic clutch in the transmission 26. In addition, thisaction blocks the inlet passage 75a to the chamber 32, and thecompressor 73 can thereby 7 build up pressure until conventional reliefmeans in the compressor bleeds the excess pressure.

When it is desired to shift the transmission from tumble to spin speed,the solenoid 88 is energized, as through suitable electrical circuitryconnected to the presettable timer means 33. Energization of thesolenoid $8 withdraws the solenoid armature 87 against the pressure ofspring means 89 to essentially the position of FIGURE 5. The airpressure from the inlet port 75, coupled with gravitational forces,moves the valve member 86 to a seating position upon surface 840 of therigid diaphragm member 84. This blocks communication between the valvechambers 82 and 83, and pressurizes both of the valve outlets 71 and'76. The outlet port 71 leads to the pneumatic clutch in thetransmission 26, causing this clutch to operate. The outlet 76 connectsto the bleed ofi valve 78, and asan off-balance load is accelerated andproduces a deflection, the bleed-off valve is intermittently opened tocause a reduction of the air pressure in the chamber 82. The reduced airpressure acting upon the pneumatic clutch causes clutch slipping and atermination of increased drum acceleration, until the off-balance loadis counterbalanced. 7

As appears in FIGURES 3 and 5, the double acting relief valve means isconstructed to provide a body portion @5 having outlet portions 95 and97 threadably receiving collar portions 93 in each of which travelsvalve core stems 99 and 99a. The valve body portion 95 is mounted onsupport means 1% (FIGURE 3) carried by a plate portion 1M welded orotherwise firmly secured to the brace members 52 and 54 of the A-frameS1. The angular position of the support means llltl relative to theplate member ltll may be adjusted by screw means 102 and The bodyportion 95 of the air valve means 78 may be adjusted linearly withrespect to support means ltlll by means of screws 102a. and 163a.

mounts a lever member res having a-claw portion lfi a engageable withthe yoke member and an end portion connected by a spring 167 to saidyoke member." As

is believed now apparent, when the support means 100 is properlyadjusted in a static condition, the yoke arm portions 105a and 105b arespaced at substantially equal distances from the valve core stems 99 and99a. When the tank and cylinder assembly starts to oscillate about itscenter of oscillation due to the acceleration of an offbalance load, theyoke member 105 will also oscillate about the pivot pin 104 driven bylever member 106. With the support means properly adjusted as stated andassuming deflection of the tank and cylinder assembly, the yoke armportions 105a and 1051) will depress the valve core stems 99 and 99a asthe casing 18 oscillates with respect to the A-frame 51 to bleed off airpressure from the pneumatic clutch in transmission 26, terminatingincreased acceleration, although maintaining the drum speed relativelyconstant for effective water balancing.

The double acting valve assembly 78 is highly advantageous as contrastedwith a single acting valve since it assures that air will be bled off ifthe machine is moved, or if the support means 100 is not properlyadjusted. In either of these circumstances, the distance between one ofthe yoke arm portions 105a and 105b and the adjacent valve stem 99 and99a would be less than the desirable setting. If the machine 10 was thenstarted up in the spin cycle with a severe off-balance load present inthe drum or cylinder 24, the machine could not accelerate since valveassembly 78 would bleed the air pressure from the pneumatic clutch on asmaller than normal movement in at least one direction of the tank andcylinder assembly. Accordingly, there would be prevented any possibilityof the machine tipping or walking under these severe conditions. Ofcourse, in order for the pneumatic clutch to again be properly actuated,the support means 100 and body portion 95 would necessarily have to beproperly ajusted with respect to yoke member 105 to the static conditionnoted.

The positioning of the valve core stems 99 and 99a with respect to theyoke member arm portions 105a and 1135b is adjustably controlled inrelation to the position of the deflector or interrupter member 66 andits associated parts so that a slightly greater deflection of the tankand cylinder assembly is required to bleed off the necessary operatingair pressure than is required to initiate the water balancing action.This is a mere matter of proper adjustment of parts and assures that thewater balancing function will be first initiated and the accelerationcontrol then set into action to maintain the transmission speed ratio atthe speed which initially caused the off balance condition and initiatedthe counterbalancing action without unnecessarily diminishing thecylinder speed.

Referring now to FIGURE 6, the transmission means 26 is provided with ahousing 110 comprising a main body portion 111 to which is secured byfastening means 112 a cap portion 113. The main body portion 111 isformed with an apertured central embossment 114 receiving therethroughvariable diameter shaft means 115 connected at one end to the motormeans 25. The apertured embossment 114 may receive bearing means 116 andseal means 117.

Axially inwardly of the bearing means 116 there is corotatably mountedupon the shaft means 115 gear means 118 in meshing relation with gearmeans 119 corotatably mounted as by pin means 119a upon shaft means 12!supported at opposite ends in bearing means 121 and 122 received inrecesses in the body portion 111 and cap portion 113, respectively.

The shaft means 120 supports for corotation gear means 123, keyed as at123a to shaft 120, meshing with gear means 124 which rotates freely at aconstant speed upon sleeve means 125 connected to the pulley 27 andsurrounding the reduced diameter portion of the shaft means 115.

Gear means 124 includes an eccentric portion 124a that has mounted on itan encircling follower strap member a that drives the piston (not shown)of the compressor 73 at a constant speed Whenever motor 25 is energized.

Gear 124 is also provided with a pocket which receives a disc insertmember 126 which is anchored to gear 124 by means of the cross pin 126a.Mounted on sleeve 125 and positioned within a cylindrical recessprovided in member 126 is a sprocket like clutch member 127 and aplurality of clutch roller members 128 which cooperate with members 126and 127 to form a one-way drive connection between these latter members.Since the oneway roller clutch formed by members 126, 127 and 128 is ofconventional construction, it will suffice to state that this connectionis made during the low or tumble speed operations when member 126 camsrollers 128 tightly against the sprocket like clutch member 127 torotate sleeve member 125 and the driven pulley 27. During the spinoperations, member 127 is driven at the speed of shaft 115 and thusoverruns disc member 126 thereby moving roller members to a disengagedposition.

Clutch member 127 is provided with a notched laterally extending flange127a which positively engages a cup or dish-shaped member 129. Locatedwithin the recess defined by member 129 is a clutch disc 139 which isprovided with friction surfaces 1315a and which is corotatable with amounting collar 131 which in turn is corotatable with and axiallymovable relative to shaft 115. Corotatably with an axially movable oncollar 131 is a second clutch disc member 132 provided with frictionsurface 132a. Corotatable with and axially movable on the cup shapedmember 129 and positioned between the clutch discs and 132 is a drivemember disc 1129a.

The means for shifting the collar member 131 to vary the rotative speedof the pulley 27, as by terminating continued acceleration when an offbalance load is detected, may comprise a yoke member 135 connected tothe collar member 131 and bearing against a fulcrum providing surface136, while being connected at its opposite end to an elongated endportion 137a on piston arm I137. The piston end portion may travel in anembossment 138 while the piston arm is guided by an apertured embossment139a formed on cylinder 139 connected to the cover member 113. Asappears in FIGURE 6, the piston arm portion 137 is connected to a headportion 140, and the cover portion 113 is apertured (not shown) toreceive the conduit means 70 for supplying air pressure to the cylinderchamber 141.

The operation of the acceleration control system of this invention maybe described as follows. As the machine proceeds from tumble to spinspeed, the solenoid 83 in the solenoid valve means 72 is energized bythe electrical circuitry in the machine. Energization of the solenoid S8withdraws the solenoid armature 17 in opposition to the pressure of thespring 59 and to essentially the position of FIGURE 5. The air pressurefrom the compressor 73 entering the inlet port 7.5, in combination withgravitational forces, moves the valve member 36 against the surface 840to block the passage 84:: between the chambers 82 and 83. The valveoutlet ports 71 and 76 are then pressurized, and as was noted, theseports lead through the conduit means 71) and 77 to the air cylinderchamber 141 in the transmission 26 and the double acting relief valve78, respectively.

Pressurization of the air cylinder chamber 141 in the transmissionhousing 116 pivots the top of yoke arm 135 to the left about fulcrum136, in FIGURE 6, which causes disc member 132 to move to the right tomove drive member disc 129a and clutch portion 139 to the right untildish shaped member 129 is driven through collar member 131 at the speedof shaft 115. This causes clutch member 127 to override disc member 126and thus drum 24 is driven at spin speed.

As the cylinder 24 rotates with an unbalanced load therein, thedeflections resulting in the drum and casing structure oscillate theyoke member 195 about the pivot pin Iii-t to intermittently actuate thevalve core stems 99- and 99a of the bleed 'ofif valve 73 which therebyreduces the pressure in the chamber 82. A reduction of the pressure inthis chamber lessens the pressure applied against the piston 146 of theair cylinder 139 and the yoke member 135 pivots in opposite directionsabout the fulcrum 136 to intermittently shift the collar member 131along the shaft 115. This action causes less pressure on disc 12% and onthe inside vertical surface of dish member 129 resulting in a slippingaction of the pneumatic clutch. However, since there is intermittentslippage in the pneumatic clutch herein provided, there is no markedspeed reduction in the pulley 27 necessarily, but merely a terminationof an increased acceleration rate. In other words, the pulley 27 whichdrives the cylinder 24 rotates at essentially the speed which caused theoff-balance condition, so that the counterbalancing action can continue.Of course, when counterbalancing is accomplished, the accelerationcontrol system reverts to the condition originally described and thesolenoid ti? is then de-energized. The action of the spring 39 thenforces the valve member 86 against the surface 82a, which permits thechamber 82 to be vented through the passage 84a and through the ventopenings $41) and 79a. In this manner the increased air pressure fromthe compressor 73 does not reach the pneumatic clutch, and since theinlet passage '75:: is blocked, a build up of pressure occurs in thecompressor 73 until the conventional relief valve therein opens.

As was earlier noted, the sensing components for the water balancesystem and for the acceleration control system are preferablycoordinated 'so that a relatively greater deflection is required toactuate the acceleration control system, than is needed to initiate thewater balancing function. Of course, an electrical sensing means couldbe used in substitution for the structure described .hereinabove, andthese and other modifications can be practiced without departing fromthe novel concepts of this invention.

The embodiments of the invention in which an ex elusive property orprivilege is claimed are defined as follows:

1. Laundry apparatus comprising, a drive motor, a support, a rotarybasket for receiving fabrics to be washed and centrifugally dried, meansmounting said basket on said support for movement in response tovibrations produced by rotation of unbalanced loads insaid basket atcentrifuging speed,

a transmission interconnecting said drive motor and said basket andhaving a low speed ratio for tum- I bling fabrics at a lower washingspeed and a high speed ratio for rotating said basket at highercentrifuging speeds for extracting fluids from said fabrics,

clutch means for changing the speed ratios of said transmission,

actuating means for said clutch means,

pressure source means including conduit means directing pressurizedfluid to said actuating means,

and valve means mounted in said conduit means,

actuator'means connected to said basket mounting means and operable uponmovement of said basket mounting means due to rotation'or" unbalancedloads at said high speed ratio to actuate said valve means for reducingthe flow of said pressurized fluid to said actuating means to shift saidclutch means and limit the speed ratio of said transmission to a valuebetween said low and said high speed ratios to thereby effect therotation of said basket at a safe optimum speed above said lower washingspeed.

2. Laundry apparatus comprising,

drive means,

support means,

a rotary basket for receiving fabrics to be washed and centrifugallydried,

means mounting said basket on said support means to accommodatevibratory movements of said basket as produced by the rotation ofacentric loads in said basket,

transmission means interconnecting said drive means and said basket toprovide a plurality of speed ratios for rotating said basket,

means providing a source of fluid pressure,

fluid clutch means controlling the selection of said speed ratios,

conduit means interconnecting said source of fluid pressure with saidfluid clutch means,

valve means in said conduit means,

valve actuator means connected to said basket mounting means andactuated'by vibratory movements of said basket to actuate said valvemeans for regulating the supply of pressure to the clutch means andthereby limiting the rotation of said basket tothose speeds whichproduce only minimal basket vibrations of a predetermined amplitude,

means for counterbalancing said acentric loads in said basket, and

control means operatively connected between the basket mounting meansand said support means and operatively engageable with said valveactuator means and said means for counterbalancing so that greateramplitudes of basket movementare required for ctuation of said valvemeans than for said counterbalancing means.

3. Laundry apparatus comprising,

drive means,

support means,

a rotary basket for receiving fabrics to be Washed and centrifugallydried,

means mounting said basket on said support means to accommodatevibratory movements of said basket as produced by the rotation 'ofacentric loads in said basket,

transmission means interconnecting said drive means and said basket toprovide aplurality of speed ratios for rotating said basket,

a fiuid compressor driven by said transmission means,

fluid clutch means in said transmission means controlling the selectionof said speed ratios,

conduit means interconnecting said compressor and I said fluid clutchmeans,

and valve means in said conduit means havingvalve actuating meansoperatively engageable with said basket mounting means and actuated byvibratoryv movements of said basket relative to said support means forregulating the supply of fluid pressure to the clutch means and therebylimiting the rotation of said basket to those optimum speeds whichproduce only minimal basket vibrations of a predetermined amplitude.

4. In a Washing machine,

a drive motor, 7

a support, 7

a rotarybasket for receiving fabrics to be Washed and centrifugallydried, i

meansmounting said basket on said support for movement in response tovibrations produced by rotation of unbalanced loads in said basket atcentrifuging speeds,

a transmission interconnecting said drive motor and said basket andhaving'means for eifecting a low speed ratio for tumbling fabrics-at alower Washing speed and means for effecting a high speed ratio clutchmeans for changing the speed ratios of said transmission,

and a pressurized fluid operated system in control of said clutch meansand said transmission and comprising valve means, valve actuating meansengageable with said basket mounting means for sensing movement of saidbasket mounting means relative to said support due to rotation ofunbalanced loads at said high speed ratio, a fluid cylinder and pistonconnected to said clutch means, and conduit means connecting said valvemeans and said fluid cylinder to a source of pressurized fluid,

said valve means being effective when an unbalanced load is rotated insaid basket at high speed ratio, and said basket mounting means isthereby in movement relative to said support, to engage said basketmounting means, thereby reducing the fluid pressure in said conduitmeans and through said clutch means actuating said transmission to limitthe speed ratio to a value between said low and said high speed ratios,thereby effecting rotation of said basket at a safe optimum speed abovesaid lower washing speed.

5. Laundry apparatus as defined in claim 1,

a fluid supply line connected to said clutch means, said valve meanscomprising a pair of bleed-off valves connected in said fluid supplyline,

said actuator means comprising a yoke member responsive to vibratorymovements of said basket and having a pair of arms respectivelypositioned adjacent said valves for alternative actuation of said valvesduring vibrations of said basket to bleed said fluid supply line tolimit the eflective speed ratio of said transmission and control therotational speed or" said basket to a safe optimum speed between a firstlower speed and a higher centrifuging speed.

6. Laundry apparatus as defined in claim 5, said fluid supply linecomprising pneumatic means, said valve means comprising pneumatic valvesconnected in parallel with one another in said fluid supply line.

7. Laundry apparatus as defined in claim 1 and further characterized bya casing,

said basket being positioned for rotation in said casing about ahorizontal axis,

a stationary support structure yieldingly mounting said casing forangular movement about an axis spaced from and parallel to saidhorizontal axis,

both of said axes being disposed in a common vertical plane intersectingsaid casing and said support structure,

a fluid line connecting said clutch means with a source of pressurizedfluid,

said valve means comprising first and second fluid pressure bleed-oivalves positioned in said fluid line and mounted on said casing to bleedoff said first fluid bleed-oil valve when said casing deflects to oneside of said vertical plane and to bleed-oil said second bleed-ofl valvewhen said casing deflects to the opposite side of said vertical plane inresponse to the rotation of unbalanced loads in said basket to limit thespeed of said drive means to an optimum level.

8. Laundry apparatus as defined in claim 1 and further characterized bythe provision of a casing,

a rigid support for said casing having sufiicient yieldability to affordlimited movement of said casing in a confined arcuate path about an axispositioned paraliel to the rotational axis of said basket,

said actuating means being responsive to movements of said casing insaid confined arcuate path.

References Cited in the file of this patent UNITED STATES PATENTS1,775,460 Herrrnann -1 Sept. 9, 1930 2,647,386 Keiper Aug. 4, 19532,760,639 Haverstock Aug. 28, 1956 2,920,496 Forster Jan. 12, 19602,950,009 Bochan Aug. 23, 1960 2,963,159 Stone Dec. 6, 1960 2,967,621Metzger Ian. 10, 1961

1. LAUNDRY APPARATUS COMPRISING, A DRIVE MOTOR, A SUPPORT, A ROTARYBASKET FOR RECEIVING FABRICS TO BE WASHED AND CENTRIFUGALLY DRIED, MEANSMOUNTING SAID BASKET ON SAID SUPPORT FOR MOVEMENT IN RESPONSE TOVIBRATIONS PRODUCED BY ROTATION OF UNBALANCED LOADS IN SAID BASKET ATCENTRIFUGING SPEED, A TRANSMISSION INTERCONNECTING SAID DRIVE MOTOR ANDSAID BASKET AND HAVING A LOW SPEED RATIO FOR TUMBLING FABRICS AT A LOWERWASHING SPEED AND A HIGH SPEED FABRIC FOR ROTATING SAID BASKET AT HIGHERCENTRIFUGING SPEEDS FOR EXTRACTING FLUIDS FROM SAID FABRICS, CLUTCHMEANS FOR CHANGING THE SPEED RATIOS OF SAID TRANSMISSION, ACTUATINGMEANS FOR SAID CLUTCH MEANS, PRESSURE SOURCE MEANS INCLUDING CONDUITMEANS DIRECTING PRESSURIZED FLUID TO SAID ACTUATING MEANS, AND VALVEMEANS MOUNTED IN SAID CONDUIT MEANS, ACTUATOR MEANS CONNECTED TO SAIDBASKET MOUNTING MEANS AND OPERABLE UPON MOVEMENT OF SAID BASKET MOUNTINGMEANS DUE TO ROTATION OF UNBALANCED LOADS